JPH02120553A - Gear device - Google Patents
Gear deviceInfo
- Publication number
- JPH02120553A JPH02120553A JP27416888A JP27416888A JPH02120553A JP H02120553 A JPH02120553 A JP H02120553A JP 27416888 A JP27416888 A JP 27416888A JP 27416888 A JP27416888 A JP 27416888A JP H02120553 A JPH02120553 A JP H02120553A
- Authority
- JP
- Japan
- Prior art keywords
- gear
- wedge body
- wedge
- auxiliary
- main
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 230000005540 biological transmission Effects 0.000 claims abstract description 17
- 238000010276 construction Methods 0.000 abstract 1
- 230000000694 effects Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 238000003780 insertion Methods 0.000 description 3
- 230000037431 insertion Effects 0.000 description 3
- 230000036544 posture Effects 0.000 description 3
- HEFNNWSXXWATRW-UHFFFAOYSA-N Ibuprofen Chemical compound CC(C)CC1=CC=C(C(C)C(O)=O)C=C1 HEFNNWSXXWATRW-UHFFFAOYSA-N 0.000 description 2
- 238000009434 installation Methods 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
Landscapes
- Gear Transmission (AREA)
- Gears, Cams (AREA)
Abstract
Description
【発明の詳細な説明】
［利用分野］
本発明は歯車装置、特に、バックラッシュを無くした歯
車装置に間するものである。 そして、この発明は、正
逆駆動する送り装置の歯車伝動部の歯車装置として特に
有効に利用できる。DETAILED DESCRIPTION OF THE INVENTION [Field of Application] The present invention relates to a gear device, particularly a gear device that eliminates backlash. The present invention can be particularly effectively used as a gear device of a gear transmission section of a forward-reverse drive feeder.
［従来技術及びその問題点］
印刷機械や工作機械においては、サーボモータによ、て
ワークを正逆駆動することが多く、この場合において、
前記サーボモータの出力軸と駆動部との間に歯車伝動装
置が採用されることも多い。[Prior art and its problems] In printing machines and machine tools, workpieces are often driven forward and backward using servo motors, and in this case,
A gear transmission is often employed between the output shaft of the servo motor and the drive section.
ところが、 通常の歯車相互をかみ
合わせる歯車伝動においては、バックラッシュが必然的
となり、このバックラッシュは伝動精度の低下を引き起
す、このことは、上記のように正逆駆動する形式の伝動
装置において特に著しいものとなる。However, in normal gear transmissions in which gears mesh with each other, backlash is inevitable, and this backlash causes a reduction in transmission accuracy. This is especially noticeable.
一方の正転のみの伝動の場合には、歯車の刃の回転方向
の背面側に常時バックラッシュに相当する隙間が生じて
も回転駆動量の精度に大きな影響を与えないが、正逆回
転を繰り返すものでは、前記バックラッシュがそのまま
駆動量のバラツキとなフて現れるからである。In the case of transmission of only one forward rotation, even if a gap equivalent to backlash always occurs on the back side of the gear blade in the rotating direction, it does not have a large effect on the accuracy of the rotational drive amount. This is because, if the drive is repeated, the backlash will directly appear as a variation in the drive amount.
かかる不都合を防止するものとして、既に、第７図及び
第８図のような形式の歯車装置がある。Gear devices of the type shown in FIGS. 7 and 8 are already available to prevent such inconveniences.
このものは、第８図に示すように、一方の歯車（１）を
２枚の補助歯車（１１）と主歯車（１２）を重ね合せた
構成として、他方の歯車（２） にかみ合わせるように
したもので、前記歯車（１）の補助歯車（１１）と主歯
車（！２）相互には、円周方向の回動付勢力を付与する
付勢手段を介装している。この付勢手段は、同軸上で回
動自在に対偶させた補助歯車（１１）と主歯車（１２）
との間にコイルバネ（Ｓ）を介装したものである。そし
て、前記補助歯車（１１）と主歯車（１２）の相対回動
域を一定の範囲に設定している。As shown in Figure 8, one gear (1) has a structure in which two auxiliary gears (11) and a main gear (12) are stacked on top of each other, and the other gear (2) meshes with the other gear (2). The auxiliary gear (11) and the main gear (!2) of the gear (1) are interposed with biasing means for applying rotational biasing force in the circumferential direction. This biasing means consists of an auxiliary gear (11) and a main gear (12) which are rotatably paired on the same axis.
A coil spring (S) is interposed between the two. The relative rotation range between the auxiliary gear (11) and the main gear (12) is set within a certain range.
このものでは、第７図のように、一方の補助歯車（１１
）に開設した円弧状小判型断面の貫通孔に他方の主歯車
（１２）のビンが突出し、このビンと前記円弧状の貫通
孔との関係によって補助歯車（１１）と主歯車（１２）
との相対回動域が一定に規制されることとなる。この相
対回動域は極小さな範囲でよく、補助歯車（１１）及び
主歯車（１２）のｉ（ｒ＋）、 （Ｔ２）相互が円周
方向に少しズレるようになっておればよい。In this case, as shown in Fig. 7, one of the auxiliary gears (11
) The pin of the other main gear (12) protrudes from the through-hole with an arc-shaped oval cross-section opened in ), and due to the relationship between this pin and the arc-shaped through-hole, the auxiliary gear (11) and the main gear (12)
The range of relative rotation with respect to this will be restricted to a certain level. This relative rotation range may be extremely small, and it is sufficient that i(r+) and (T2) of the auxiliary gear (11) and the main gear (12) are slightly shifted from each other in the circumferential direction.
この従来のものでは、第８図のように歯車（１）と歯車
（２）とがかみ合わされた状態では、第９図のように各
歯車相互のバックラッシュに応じたズレが歯（Ｔ＋）と
１（Ｔ２）との間に生じた状態で回転伝動する。従って
、前、記バックラッシュが生じないこととなる。即ち、
一方への回転伝動の際には、主歯車（１２）のみを介し
て歯車（１）のボス（１０）に回転力が伝動され、逆方
向の回転の際には、補助歯車（１１）からコイルバネ（
Ｓ）を介して主歯車（１２）に回転力が伝動されること
となる。In this conventional type, when the gear (1) and the gear (2) are meshed as shown in Fig. 8, the misalignment corresponding to the mutual backlash between the gears occurs as shown in Fig. 9. Rotation is transmitted in the state that occurs between and 1 (T2). Therefore, the above-mentioned backlash does not occur. That is,
When rotating in one direction, the rotational force is transmitted to the boss (10) of the gear (1) only through the main gear (12), and when rotating in the opposite direction, it is transmitted from the auxiliary gear (11). Coil spring (
The rotational force is transmitted to the main gear (12) via S).
ところが、この従来のものでは、前記コイルバネ（Ｓ）
からなる付勢手段の装着が面倒であるとともに、一方へ
の回転伝動の際の伝動力（例えば、コイルバネ（Ｓ）を
介して補助歯車（１１）から主歯車（１２）に回転力が
伝動される際の伝動力）を犬きく設定できない、という
問題がある。However, in this conventional one, the coil spring (S)
It is troublesome to attach the biasing means consisting of the There is a problem in that it is not possible to precisely set the transmission force when
今、主歯車（１２）が歯車（２）に直接かみ合うときを
正転状態とし、これとは逆に補助歯車（１１）が直接歯
車（２） にかみ合うときを逆転状態とすると、逆転状
態においては、歯車（１）から歯車（２）への伝動力は
一義的にはコイルバネ（Ｓ）の付勢力によってのみ伝達
されることとなるからであり、この付勢力を大きくしよ
うとすると、コイルバネ（Ｓ）の数を増やすか又はそれ
ぞれのコイルバネ（Ｓ）の付勢力を極端に大きくする必
要があり、前者の場合には、歯車（１）の構成が複雑に
なる。Now, when the main gear (12) directly meshes with the gear (2), it is called a forward rotation state, and when the auxiliary gear (11) directly meshes with the gear (2), it is called a reverse rotation state. This is because the transmission force from gear (1) to gear (2) is primarily transmitted only by the biasing force of the coil spring (S), and if you try to increase this biasing force, the coil spring (S) It is necessary to increase the number of coil springs (S) or to extremely increase the biasing force of each coil spring (S), and in the former case, the configuration of the gear (1) becomes complicated.
又、後者の場合には、コイルバネ（Ｓ）の装着が面倒な
ものとなる。この結果逆転状態における伝動トルクを大
かく設定できないのが実情である。Moreover, in the latter case, it becomes troublesome to attach the coil spring (S). As a result, the actual situation is that it is not possible to set a large amount of transmission torque in the reversed state.
［ｉ！題］
本発明は、このような、「歯車（１）及び歯車（２）を
かみ合わせて両方の歯車を正逆方向に伝動させ、一方の
歯車（１） を、共に歯車（２） にかみ合う二枚型ね
構造の補助歯車（１１）と主歯車（１２）とから構成す
るとともに補助歯車（１１）と主歯車（１２）の相互を
一定範囲相対回動可能に対偶させ、前記相対回動方向に
付勢する付勢手段を前記補助歯車（１１）と主歯車（１
２）との間に介装し、一方の主歯車（１２）を直接軸に
装着するようにした歯車装置」において、主歯車（１２
）が補助歯車（１１）を介して伝動される上記逆転状態
における伝動力を大きくできるようにするとともに前記
付勢手段の装着を簡単にすることを課題ξする。[i! [Problem] The present invention is based on the above-mentioned method, in which gear (1) and gear (2) are meshed to transmit transmission in forward and reverse directions, and one gear (1) is meshed with gear (2). It is composed of an auxiliary gear (11) and a main gear (12) having a plate-shaped screw structure, and the auxiliary gear (11) and the main gear (12) are paired so that they can rotate relative to each other within a certain range, and the relative rotation direction is A biasing means for biasing the auxiliary gear (11) and the main gear (1)
2), and one of the main gears (12) is mounted directly on the shaft.
) is transmitted through the auxiliary gear (11) in the above-mentioned reversed state, and it is an object of the present invention to make it possible to increase the transmission force in the above-mentioned reversed state, and to simplify the mounting of the above-mentioned urging means.
［技術的手段］
上記課題を解決するために講じた本発明の技術的手段は
「補助歯車（１１）と主歯車（１２）の互いに対向する
位置にこれらの回転面に対して略直角方向の貫通孔部（
３１）及び貫通孔部（３２）を形成し、一方の貫通孔部
（３１）に第１楔体（４１）を挿入するとともに他方の
貫通孔部（３２）に第２楔体（４２）を挿入し、上記付
勢手段を、前記第１楔体（４１）及び第２楔体（４２）
、これらの楔体相互を軸線方向に貫通し且これの締付け
によって前記第１楔体（４１）及び第２楔体（４２）を
相互に接近させる締付はボルト（５）、及びこれの締付
は力を一定に設定し且前記締付はボルト（５）と第１楔
体（４１）又は第２楔体（４２）との間に介装されたバ
ネ（Ｂ）とから構成し、前記付勢手段は前記締付はボル
ト（５）の締付けに伴なう第１楔体（４１）及び第２楔
体（４２）の相互接近によってこれら楔体が補助歯車（
１１）と主歯車（１２）を相互に円周方向反対側に圧接
すべく前記楔体相互が又は楔体と貫通孔部とが傾斜面を
介して対接するようにしたヨことである。[Technical Means] The technical means of the present invention taken to solve the above problems is as follows. Through-hole (
31) and a through-hole portion (32), a first wedge body (41) is inserted into one through-hole portion (31), and a second wedge body (42) is inserted into the other through-hole portion (32). inserting the biasing means into the first wedge body (41) and the second wedge body (42).
, the bolt (5) passes through these wedge bodies mutually in the axial direction and is tightened to bring the first wedge body (41) and the second wedge body (42) closer to each other. The tightening force is set constant, and the tightening consists of a spring (B) interposed between the bolt (5) and the first wedge body (41) or the second wedge body (42), The biasing means causes the first wedge body (41) and the second wedge body (42) to approach each other as the bolt (5) is tightened, so that these wedge bodies are connected to the auxiliary gear (
11) and the main gear (12) are brought into pressure contact with each other on opposite sides in the circumferential direction, so that the wedge bodies or the wedge body and the through-hole portion are brought into contact with each other via an inclined surface.
［作用］ 本発明の上記技術的手段は次のように作用する。[Effect] The above technical means of the present invention operates as follows.
補助歯車（１１）と主歯車（１２）には相互に対向する
位置に貫通孔部（３１）、 （３２）が形成され、これ
に付勢手段を挿入して締付はボルト（５）を所定のトル
クで締付けるだけで補助歯車（１１）と主歯車（１２）
からなる歯車（１）としての組立体が完成する。Through holes (31) and (32) are formed in the auxiliary gear (11) and the main gear (12) at positions facing each other, and a biasing means is inserted into these holes and tightened by tightening the bolt (5). The auxiliary gear (11) and main gear (12) can be separated by simply tightening them to the specified torque.
The assembly as a gear (1) is completed.
この歯車（１）を歯車（２）にかみ合わせると、締付は
ボルト（５） の締付は力に対応するバネＣＢ）の付勢
力に応じて第１楔体（４１）と第２撲体（４２）の相互
が接近する方向に加圧され、この加圧力に応じた圧接力
で、第１楔体（４１）及び第２楔体（４２）がそれぞれ
対応する貫通孔部の側壁（補助歯車（１１）又は主歯車
（１２）の円周方向の側壁）に対接し、補助歯車（１１
）及び主歯車（１２）を円周方向反対側に付勢する。When this gear (1) is meshed with the gear (2), the bolt (5) is tightened according to the urging force of the spring CB (corresponding to the force) between the first wedge body (41) and the second wedge body (41). Pressure is applied in the direction in which the bodies (42) approach each other, and a pressing force corresponding to this pressurizing force causes the first wedge body (41) and the second wedge body (42) to press against the side wall ( The auxiliary gear (11) is in contact with the side wall in the circumferential direction of the auxiliary gear (11) or the main gear (12).
) and the main gear (12) in opposite directions in the circumferential direction.
歯車（１）の逆転状態では、歯車（２）と補助歯車（１
１）とが直接かみ合って第１楔体（４１）ロパネ（８）
口第２楔体（４２）−＞主歯車（１２）の経路でトルク
が伝達されることとなるが、このとき、楔体相互又は各
楔体の傾斜面と貫通孔部の傾斜面との対接部に作用する
補助歯車（１１）と主歯車（１２）の相対回動力（圧接
力）の小さな分力がバネ（Ｂ）に作用する。When gear (1) is in a reversed state, gear (2) and auxiliary gear (1)
1) are directly engaged with the first wedge body (41) and the lopane (8)
Torque is transmitted along the path from the second wedge body (42) to the main gear (12), but at this time, the relationship between the wedge bodies or between the inclined surfaces of each wedge body and the inclined surface of the through hole portion is transmitted. A small component of the relative rotational force (pressing force) between the auxiliary gear (11) and the main gear (12) acting on the opposing portion acts on the spring (B).
従って、これに対抗する付勢力を前記バネ（Ｂ）に具備
させれば歯車（１）の逆転時における第１・主歯車相互
の相対回動が阻止されるから、バネ（Ｂ）自体の付勢力
が小さいものであっても、前記相対回動力を阻止できる
こととなる。Therefore, if the spring (B) is provided with a biasing force that opposes this, the relative rotation of the first and main gears when the gear (1) is reversed is prevented, so that the biasing force of the spring (B) itself is prevented. Even if the force is small, the relative rotational force can be blocked.
［効果］ 本発明は上記構成であるから次の特有の効果を有する。[effect] Since the present invention has the above configuration, it has the following unique effects.
バネ（Ｂ）の付勢力が小さなものであっても、補助歯車
（１１）と主歯車（１２）との相対回動阻止力が得られ
るものとなるから、逆転状態における伝動トルクが大き
くなる。Even if the biasing force of the spring (B) is small, a force for preventing relative rotation between the auxiliary gear (11) and the main gear (12) can be obtained, so the transmission torque in the reverse state becomes large.
貫通孔部（Ｈ）、 （３２）に付勢手段を挿入して締付
はボルト（５）を所定のトルクで締付けるだけで補助歯
車（１１）と主歯車（１２）からなる歯車（１）として
の組立体が完成するから、付勢手段の装着が簡単である
。To tighten the gear (1) consisting of the auxiliary gear (11) and the main gear (12), simply insert the biasing means into the through holes (H) and (32) and tighten the bolt (5) to the specified torque. Since the assembly is completed, it is easy to attach the biasing means.
［実施例］
以下、本発明の実施例を第１図から第６図に基いて説明
する。[Example] Hereinafter, an example of the present invention will be described based on FIGS. 1 to 6.
■、第１実施例について
第１図〜第３図に示す第１実施例のものは、第１楔体（
４１）及び第２楔体（４２）をこれらを収容する貫通孔
部（３１）及び貫通孔部（３２）に各別に模対偶（移動
方向に対して傾斜する傾斜面相互が対接する対偶関係）
に設定したものであり、第１図に示すように、貫通孔部
（３１）の一方の側壁は傾斜面（３３）となり、貫通孔
部（３２）の一方の側壁が傾斜面（３４）となつて、こ
れら傾斜面（３３）及び傾斜面（３４）は相互に補助歯
車（１１）及び主歯車（１２）の円周方向の反対側に位
置する。このため、各貫通孔部はその断面形状が第２琴
に示すように円弧状小判型となっている。(2) Regarding the first embodiment The first embodiment shown in FIGS. 1 to 3 has a first wedge body (
41) and the second wedge body (42) respectively in the through-hole portion (31) and the through-hole portion (32) that house them (a pairing relationship in which the inclined surfaces inclined with respect to the moving direction are in contact with each other).
As shown in Fig. 1, one side wall of the through hole section (31) becomes an inclined surface (33), and one side wall of the through hole section (32) becomes an inclined surface (34). Thus, the inclined surface (33) and the inclined surface (34) are located on opposite sides of the auxiliary gear (11) and the main gear (12) in the circumferential direction. Therefore, each through-hole has a cross-sectional shape of an arcuate oval shape as shown in the second koto.
前記第１楔体（４１）及び第２楔体（４２）は同様の構
成であり、第３図のように、締付はボルト（５）を挿通
させるフランジ部（４０）の約半分の範囲から楕円テー
バ半体（４５）を突出させたもので、この楕円テーバ半
体（４５）の表面が前記傾斜面（３３）に対接するよう
になっている。又、この楕円テーバ半体（４５）の反対
側は締付はボルト（５）の挿通部の中心と一致する平面
部（４６）となっている、従フて、同じ構成の第１楔体
（４１）と第２楔体（４２）とを反対の姿勢で対向させ
ると、前記平面部（４［ｉｌ、 （４６）相互が摺動
可能に対接することとなり、しかも、この状態では、前
記両方の楔体の締付はボルト（５）を挿通させる挿通孔
相互が同軸上に位置することとなる。The first wedge body (41) and the second wedge body (42) have the same structure, and as shown in FIG. An elliptical taber half body (45) is projected from the elliptical taber half body (45), and the surface of this elliptical taber half body (45) is in contact with the inclined surface (33). Further, the opposite side of this elliptical tapered half body (45) is a flat part (46) that coincides with the center of the insertion part of the bolt (5) for tightening. (41) and the second wedge body (42) face each other in opposite postures, the plane portions (46) will come into sliding contact with each other, and in this state, the When both wedge bodies are tightened, the insertion holes through which the bolts (5) are inserted are positioned coaxially with each other.
さらに、バネ（８）としては皿バネを採用し、この皿バ
ネが締付はボルト（５）の頭部（５１）と第２模体（４
２）との間と、締付はボルト（５） に螺合されるナツ
ト（５２）と第１楔体（４１）との間に介装されている
。これにより、締付はボルト（５）を締付けた状態では
前記両方の皿バネの付勢力に応じた対向接近力が第１楔
体（４１）と第２楔体（４２）に作用することとなる。Furthermore, a disc spring is used as the spring (8), and this disc spring tightens the head (51) of the bolt (5) and the second body (4).
2) and the nut (52) screwed onto the bolt (5) and the first wedge body (41). As a result, when the bolt (5) is tightened, opposing approach forces corresponding to the biasing forces of both disc springs act on the first wedge body (41) and the second wedge body (42). Become.
この実施例では、貫通孔部（３１）及び貫通孔部（３２
）の組が第２図のように四組対称位置に配設され、各貫
通孔部に上記した第１楔体（４１）、第２楔体（４２）
、締付はボルト（５）及び皿バネの組み合せからなる付
勢手段が収容されることとなる。In this embodiment, the through hole portion (31) and the through hole portion (32
) are arranged in symmetrical positions as shown in FIG.
For tightening, a biasing means consisting of a combination of a bolt (5) and a disc spring is accommodated.
尚、上記傾斜面（３３）及び傾斜面（３４）は共に歯車
（１）の両側面外側に向く傾斜面としてあり、皿バネに
よる付勢力が作用した状態において補助歯車（１１）と
主歯車（１２）の対接面には前記傾斜面と第１楔体（４
１）及び第２楔体（４２）の楕円テーバ半体（４５）と
の圧接力による分力がこれらの歯車相互を圧接する方向
に作用することから、伝動時におりる補助歯車（１１）
と主歯車（１２）の一体化が促進される。この点からも
、歯車（１）の逆転時におけるバックラッシュが生じに
くいものとなる。Incidentally, both the inclined surface (33) and the inclined surface (34) are inclined surfaces facing outward on both sides of the gear (1), and when the biasing force of the disc spring is applied, the auxiliary gear (11) and the main gear ( 12), the inclined surface and the first wedge body (4
1) and the second wedge body (42) with the elliptical taber half body (45) acts in a direction that presses these gears together, so that the auxiliary gear (11) descends during transmission.
The integration of the main gear (12) and the main gear (12) is promoted. Also from this point of view, backlash is less likely to occur when the gear (1) is reversed.
なお、この実施例において、貫通孔部（３１）及び貫通
孔部（３２）の断面形状を円弧状に屈曲する小判型とし
たが、補助歯車（１１）と主歯車（１２）の相対回動量
は極少いものであるから、この断面形状を直線状の小判
型としてもよい。In addition, in this example, the cross-sectional shape of the through-hole portion (31) and the through-hole portion (32) is an oval shape bent in an arc shape, but the relative rotation amount between the auxiliary gear (11) and the main gear (12) Since this is extremely small, the cross-sectional shape may be a linear oval shape.
■、第２実施例について
次に第４図〜第６図に示す第２実施例のものは、第１楔
体（４１）と第２楔体（４２）の相互を傾斜面（４３）
によって対接させるようにしたものであり、貫通孔部（
３１）及び貫通孔部（３２）を共に円形透孔としたもの
である。この実施例のものも、第５図に示すように上記
第１実施例と同様に複数の付勢手段が歯車（１）の平面
部中程の対称位置に開口するように配設される。(2) Regarding the second embodiment Next, in the second embodiment shown in Figs.
The through hole part (
31) and the through hole portion (32) are both circular through holes. In this embodiment as well, as shown in FIG. 5, a plurality of biasing means are arranged to open at symmetrical positions in the middle of the plane portion of the gear (1), similar to the first embodiment.
第１楔体（４１）及び第２楔体（４２）は共に同様な構
成となっており、第６図に示すように、筒部（４４）の
一端から先端側に向く姿勢の傾斜面（４３）を具備する
楔部（４７）を突出形成したもので、この傾斜面（４３
）は、第１楔体（４１）及び第２楔体（４２）の中心線
と交叉する平面上に位置する。Both the first wedge body (41) and the second wedge body (42) have the same configuration, and as shown in FIG. 6, the inclined surface ( A wedge portion (47) having a wedge portion (43) is formed protrudingly from the inclined surface (43).
) is located on a plane that intersects the center lines of the first wedge body (41) and the second wedge body (42).
そして、これら第１模体（４１）及び第２楔体（４２）
を貫通する締付はボルト（５）は、頭部（５１）の端面
に形成した六角形状の凹陥部に工具を対応させるように
したもので、一方の第１楔体（４１）には、前記頭部（
５１）を収容する凹陥部（４８）が形成されており、他
方の第２楔体（４２）の筒部（４４）には、締付はボル
ト（５）のネジ部が螺合する雌ネジ部（４９）が形成さ
れている。又、上記楔部（４７）の内側部分即ち傾斜面
（４３）の形成部の中央には半円形断面のボルト挿通溝
（５０）が形成されている。And these first model (41) and second wedge body (42)
For tightening the bolt (5) through the head (51), the tool is adapted to fit into a hexagonal recess formed on the end face of the head (51). The head (
A recessed part (48) is formed to accommodate the bolt (51), and the cylindrical part (44) of the other second wedge body (42) has a female screw thread into which the threaded part of the bolt (5) is screwed. A portion (49) is formed. Further, a bolt insertion groove (50) with a semicircular cross section is formed in the inner part of the wedge part (47), that is, in the center of the part where the inclined surface (43) is formed.
従って、第４図のように、第１楔体（４１）及び第２楔
体（４２）を貫通孔部（３１）と貫通孔部（３２）に各
別に収容して締付はボルト（５）を第１楔体（４１）か
ら貫通させて第２楔体（４２）の雌ネジ部に螺合させ、
頭部（５１）と第１楔体（４１）の端面との間にバネ（
Ｂ）としての皿バネを介装しておくと、締付はボルト（
５）の締付は力に応じた付勢力が皿バネを介して第１楔
体（４１）と第２楔体（４２）の相互間に作用すること
となり、この付勢力に応じた作用力で傾斜面（４３）、
（４３）相互が圧接され、これに応じて楔部（４７
）、 （４７）相互には斥力が作用して筒部（４４）
の側壁は貫通孔部（３１）及び貫通孔部（３２）のそれ
ぞれの側壁を歯車（１）の円周方向反対側に圧接するこ
ととなり、上記第１実施例と同様に機能する。Accordingly, as shown in FIG. ) is penetrated from the first wedge body (41) and screwed into the female threaded part of the second wedge body (42),
A spring (
If a disc spring is inserted as B), the tightening can be done using the bolt (
In the tightening of 5), a biasing force corresponding to the force acts between the first wedge body (41) and the second wedge body (42) via the disc spring, and an acting force corresponding to this biasing force is generated. slanted surface (43),
(43) They are pressed against each other, and the wedge portion (47
), (47) A repulsive force acts on each other and the cylindrical part (44)
The side walls of the through hole portion (31) and the through hole portion (32) are brought into pressure contact with the side walls of the through hole portion (31) and the through hole portion (32) on the opposite side in the circumferential direction of the gear (1), and functions in the same manner as in the first embodiment.
また、締付はボルト（５）の締付は力の一部が第１楔体
（４１）及び第２楔体（４２）を介して補助歯車（１１
）と主歯車（１２）の対接面に作用することとなり、こ
の点でも、両歯車が上記ｙｇ１実施例と同様に相対回動
しにくいものとなる。In addition, when tightening the bolt (5), part of the force is transferred to the auxiliary gear (11) via the first wedge body (41) and the second wedge body (42).
) and the main gear (12), and in this respect as well, both gears are difficult to rotate relative to each other, similar to the above yg1 embodiment.
尚、第１楔体（４１）と貫通孔部（３１）の嵌合公差及
び第２楔体（４２）と貫通孔部（３２）の嵌合公差はＪ
ＩＳ−ｈ７Ｈ７程度でよい。In addition, the fitting tolerance between the first wedge body (41) and the through hole portion (31) and the fitting tolerance between the second wedge body (42) and the through hole portion (32) are J.
IS-h7H7 or so is sufficient.
上記実施例では貫通孔部（３１）及び第１楔体（４１）
等を共に円形断面の構成としたが、第１楔体（４１）及
び第２模体（４２）の挿入姿勢を適正にしてその傾斜面
（４３）が円周方向を向くように装着すれば、締付はボ
ルト（５）の締付は状態において、貫通孔（３１）、
（３２）相互が僅かにズレることから、前記取付は姿
勢が伝動中に変化することはない、尚、貫通孔（３１）
、 （３２）及び各楔体の断面を楕円状断面にしてその
長径を歯車（１）の円周方向に一致させ、さらに、傾斜
面（４３）が前記長径の方向に向く面としておけば、締
付はボルト（５）の締付は状態において筒部（４４）の
側壁の貫通孔部（３１）又は貫通孔部（３２）への対接
方向は歯車（１） の円周方向に正確に一致したものと
なるとともに、伝動状態において前記対接部がズしたり
する心配がない。In the above embodiment, the through hole portion (31) and the first wedge body (41)
Both of them have a circular cross section, but if the first wedge body (41) and the second wedge body (42) are inserted in an appropriate posture and are installed so that their inclined surfaces (43) face in the circumferential direction. , when tightening the bolt (5), tighten the through hole (31),
(32) Since the two are slightly shifted from each other, the posture of the above-mentioned installation will not change during transmission. Furthermore, the through hole (31)
, (32) and if the cross section of each wedge body is made into an elliptical cross section and its major axis coincides with the circumferential direction of the gear (1), and furthermore, the inclined surface (43) is a surface facing in the direction of the major axis, When tightening the bolt (5), ensure that the direction of contact with the through hole (31) or through hole (32) in the side wall of the cylinder part (44) is accurate in the circumferential direction of the gear (1). In addition, there is no fear that the abutting portions will shift during the transmission state.
特に、この実施例のものでは、第１楔体（４１）及び第
２楔体（４２）の楔部（４７）の中程より先端側（最終
締付は状態において相手側の歯車部分侵入する範囲）の
半径を筒部（４４）のそれに比べて僅かに小径に設定し
、他方の貫通孔部（３１）及び貫通孔部（３２）の直径
を前記筒部（４４）と所定の嵌合公差となるようにしで
あるから、締付はボルト（５）を締付けた状態において
、小径部から大径部への変化部が相手側の貫通孔部（３
１）又は貫通孔部（３２）の内側の端縁に外側から係合
することとなり、第１楔体（４１）と第２楔体（４２）
の組立体が貫通孔部（３１）及び貫通孔部（３２）から
なる貫通孔部内に抜止め状態に保持される。In particular, in this embodiment, the wedge portions (47) of the first wedge body (41) and the second wedge body (42) are on the tip side from the middle (the final tightening is done when the gear portion of the other party enters). range) is set to be slightly smaller than that of the cylindrical portion (44), and the diameters of the other through-hole portion (31) and through-hole portion (32) are set to a predetermined fit with the cylindrical portion (44). Since the bolt (5) is tightened to meet the tolerance, when the bolt (5) is tightened, the transition part from the small diameter part to the large diameter part should be tightened so that the part where the diameter changes from the small diameter part to the large diameter part is the through hole part (3) on the other side.
1) or the inner edge of the through hole portion (32) from the outside, and the first wedge body (41) and the second wedge body (42)
The assembly is held in a secured state within a through-hole section consisting of a through-hole section (31) and a through-hole section (32).
尚、ここで、第１楔体（４１）の筒部（４４）に形成し
た締付はボルト挿通用の透孔と締付はボルト（５）の軸
部との間には、嵌合余裕を設けであることは言うまでも
ない、この嵌合余裕があることから、第１楔体（４１）
及第２楔体（４２）が相互に円周方向に移動可能となる
のである。Note that there is a fitting margin between the through hole formed in the cylindrical portion (44) of the first wedge body (41) for inserting the tightening bolt and the shaft portion of the tightening bolt (5). It goes without saying that the first wedge body (41)
This allows the second wedge body (42) to move relative to each other in the circumferential direction.
第１図は第１実施例の要部断面図で第２図のＸ−Ｘ断面
図、第２図は第１実施例の正面図、第３図はこれに用い
る楔体の説明図、第４図は第２実施例の要部断面図で第
５図のＹ−Ｙ断面図第５図は第２実施例の正面図、第６
図はこれに用いる楔体の説明図、第７図〜第９図は従来
例の説明図であり、図中。
（１） ・・・・歯車
（２） ・・・・歯車
（１１）・・・・補助歯車
（１２）・・・・主歯車
（３ｘ） 、 （３２） ・貫通孔部（４１）・・・
・第１楔体
（４２）・・・・第２楔体
（５）・・・・締付はボルト
ＣＢ＋ ・ ・ ・・バネFig. 1 is a sectional view of the main part of the first embodiment, and a sectional view taken along line XX in Fig. 2, Fig. 2 is a front view of the first embodiment, and Fig. 3 is an explanatory diagram of the wedge body used in this. Figure 4 is a cross-sectional view of the main part of the second embodiment, and Figure 5 is a Y-Y cross-sectional view of the second embodiment.
The figure is an explanatory diagram of a wedge body used in this, and FIGS. 7 to 9 are explanatory diagrams of a conventional example. (1) ... Gear (2) ... Gear (11) ... Auxiliary gear (12) ... Main gear (3x), (32) - Through hole (41) ...・
・First wedge body (42)...Second wedge body (5)...Tighten with bolt CB+...Spring
Claims (1)
正逆方向に伝動させ、一方の歯車（１）を、共に歯車（
２）にかみ合う二枚重ね構造の補助歯車（１１）と主歯
車（１２）とから構成するとともに補助歯車（１１）と
主歯車（１２）の相互を一定範囲相対回動可能に対偶さ
せ、前記相対回動方向に付勢する付勢手段を前記補助歯
車（１１）と主歯車（１２）との間に介装し、一方の主
歯車（１２）を直接軸に装着するようにした歯車装置に
おいて、補助歯車（１１）と主歯車（１２）の互いに対
向する位置にこれらの回転面に対して略直角方向の貫通
孔部（３１）及び貫通孔部（３２）を形成し、一方の貫
通孔部（３１）に第１楔体（４１）を挿入するとともに
他方の貫通孔部（３２）に第２楔体（４２）を挿入し、
上記付勢手段を、前記第１楔体（４１）及び第２楔体（
４２）、これらの楔体相互を軸線方向に貫通し且これの
締付けによって前記第１楔体（４１）及び第２楔体（４
２）を相互に接近させる締付けボルト（５）、及びこれ
の締付け力を一定に設定し且前記締付けボルト（５）と
第１楔体（４１）又は第２楔体（４２）との間に介装さ
れたバネ（Ｂ）とから構成し、前記付勢手段は前記締付
けボルト（５）の締付けに伴なう第１楔体（４１）及び
第２楔体（４２）の相互接近によってこれら楔体が補助
歯車（１１）と主歯車（１２）を相互に円周方向反対側
に圧接すべく前記楔体相互が又は楔体と貫通孔部とが傾
斜面を介して対接するようにした歯車装置。Gear (1) and gear (2) are meshed to transmit transmission in forward and reverse directions, and one gear (1) is engaged with both gears (
2) consists of an auxiliary gear (11) and a main gear (12) having a two-ply structure that mesh with each other, and the auxiliary gear (11) and the main gear (12) are paired so that they can rotate relative to each other within a certain range, and the relative rotation A gear device in which a biasing means for biasing in the moving direction is interposed between the auxiliary gear (11) and the main gear (12), and one of the main gears (12) is mounted directly on the shaft, A through-hole portion (31) and a through-hole portion (32) are formed at positions where the auxiliary gear (11) and the main gear (12) face each other in a direction substantially perpendicular to their rotating surfaces, and one through-hole portion is formed. Insert the first wedge (41) into (31) and insert the second wedge (42) into the other through hole (32),
The biasing means is connected to the first wedge body (41) and the second wedge body (
42), the first wedge body (41) and the second wedge body (42) pass through each other in the axial direction and are tightened.
2) a tightening bolt (5) that brings the two parts closer to each other, and a tightening force thereof set at a constant value, and between the tightening bolt (5) and the first wedge body (41) or the second wedge body (42). and an interposed spring (B), and the biasing means is activated by the first wedge body (41) and the second wedge body (42) approaching each other as the tightening bolt (5) is tightened. In order for the wedge bodies to press the auxiliary gear (11) and the main gear (12) against each other on opposite sides in the circumferential direction, the wedge bodies or the wedge body and the through hole portion are brought into contact with each other via an inclined surface. gearing.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP27416888A JPH02120553A (en) | 1988-10-28 | 1988-10-28 | Gear device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP27416888A JPH02120553A (en) | 1988-10-28 | 1988-10-28 | Gear device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH02120553A true JPH02120553A (en) | 1990-05-08 |
Family
ID=17537984
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP27416888A Pending JPH02120553A (en) | 1988-10-28 | 1988-10-28 | Gear device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH02120553A (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5152186A (en) * | 1990-08-14 | 1992-10-06 | Man Roland Druckmaschinen | Gearwheel for the drive of offset press cylinders |
| US8562474B2 (en) | 2011-03-22 | 2013-10-22 | Seiko Epson Corporation | Speed reducer, robot hand and robot |
| US8568264B2 (en) | 2011-03-23 | 2013-10-29 | Seiko Epson Corporation | Speed reducer, robot hand and robot |
| US8651992B2 (en) | 2011-03-22 | 2014-02-18 | Seiko Epson Corporation | Speed reducer, robot hand and robot |
| US8840513B2 (en) | 2011-03-22 | 2014-09-23 | Seiko Epson Corporation | Speed reducer, robot hand and robot |
| CN104626730A (en) * | 2013-11-13 | 2015-05-20 | 海德堡印刷机械股份公司 | An apparatus for electrically driving a gear |
| CN105864396A (en) * | 2016-05-01 | 2016-08-17 | 保定标正机床有限责任公司 | Gear clearance removing mechanism |
| CN106402363A (en) * | 2016-11-10 | 2017-02-15 | 北京特种机械研究所 | Gear transmission return clearance eliminating structure |
-
1988
- 1988-10-28 JP JP27416888A patent/JPH02120553A/en active Pending
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5152186A (en) * | 1990-08-14 | 1992-10-06 | Man Roland Druckmaschinen | Gearwheel for the drive of offset press cylinders |
| US8562474B2 (en) | 2011-03-22 | 2013-10-22 | Seiko Epson Corporation | Speed reducer, robot hand and robot |
| US8651992B2 (en) | 2011-03-22 | 2014-02-18 | Seiko Epson Corporation | Speed reducer, robot hand and robot |
| US8840513B2 (en) | 2011-03-22 | 2014-09-23 | Seiko Epson Corporation | Speed reducer, robot hand and robot |
| US8568264B2 (en) | 2011-03-23 | 2013-10-29 | Seiko Epson Corporation | Speed reducer, robot hand and robot |
| CN104626730A (en) * | 2013-11-13 | 2015-05-20 | 海德堡印刷机械股份公司 | An apparatus for electrically driving a gear |
| CN105864396A (en) * | 2016-05-01 | 2016-08-17 | 保定标正机床有限责任公司 | Gear clearance removing mechanism |
| CN106402363A (en) * | 2016-11-10 | 2017-02-15 | 北京特种机械研究所 | Gear transmission return clearance eliminating structure |
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